Rotor vane motor device

ABSTRACT

An eccentric rotor, concentric vane motor device characterized by one or more of the following improvements: (1) an improved seal structure for sealing between the vanes and rotor vane guides as they rotate and interdigitate the vanes within a main chamber; (2) an adjustable inlet aperture on a torque control sleeve to eliminate a throttle and its associated loss in efficiency; (3) adjustable exhaust apertures in an exhaust control to reduce losses from over- or under-expansion of a working fluid flowing through the motor; (4) a combination of the adjustable inlet aperture and the adjustable exhaust apertures to enable optimum efficiency, including the supercharging capability, over a wide range of power and speed requirements; and (5) a vane tip seal intermediate the vane and the interior cylindrical surface of a main chamber within which the vanes rotate. The motor device is employed in a system, including a reversing valve arrangement, for reversing the direction of rotation of the motor; and has within it means for reversibly positioning the adjustable inlet apertures and the adjustable exhaust apertures. Also disclosed are specific embodiments useful for a wide variety of working fluids, regardless of whether or not the working fluids are recirculated.

United States Patent 1 1 Keller ROTOR VANE MOTOR DEVICE [75] Inventor:Leonard J. Keller, Sarasota, Fla.

[73] Assignee: The Keller Corporation, Sarasota,

Fla.

[22] Filed: Feb. 18, 1972 [21] Appl. No.: 227,393

[52] US. Cl 418/137, 418/159, 418/241 [51] Int. Cl. FOlc 1/00, FOlc19/00, F04c 27/00 [58] Field of Search 418/33, 35, 37, 136, 137,418/138, 145,159, 241, 253, 234

[56] References Cited UNlTED STATES PATENTS 32,029 4/1861 Johnson418/241 3,066,851 12/1962 Marshal1.... 418/159 1 Mar. 19, 1974 PrimaryEraminer-Carltor'i Croyle Assistant Examiner-John J. Vrablik Attorney,Agent, or Firm-Wofford, Felsman & Fails [5 7 ABSTRACT An eccentricrotor, concentric vane motor device characterized by one or more "of thefollowing improvements: (1) an improved seal structure for sealingbetween the vanes and rotor vane guides as they rotate and interdigitatethe vanes within a main chamber;-(2) an adjustable inlet aperture on atorque control sleeve to eliminate a throttle and its associated loss inefficiency; (3) adjustable exhaust apertures in an exhaust control toreduce losses from overor under-expansion of a working fluid flowingthrough the motor; (4) a combination of the adjustable inlet apertureand the adjustable exhaust apertures to enable optimum efficiency,including the supercharging capability, over a wide range of power andspeed requirements; and (5) a vane tip seal intermediate the vane andthe interior cylindrical surface of a main chamber within which thevanes rotate. The motor device is employed in a system, including areversing valve arrangement, for reversing the direction of rotation ofthe motor; and has within it means for reversibly positioning theadjustable inlet apertures and the adjustable exhaust apertures. Alsodisclosed are specific embodiments useful for a wide variety of workingfluids, regardless of whether or not the working fluids arerecirculated.

9 Claims, 20 Drawing Figures PAIENTEDNAR 1 9 1914 SHEU 1 Bf 7 Q n QQGNRPAIENTEB m 19 1914 SHEET 3 [IF 7 20 PRIOR ART PATENTED 9 1974 SHEET 0F 7PAIENIEDHAR 1 a 1924 3. 7 97'. 97 5 SHEET E OF 7 T .225 LOW PRESSURE WRECEIVER HIGH I PRESSURE :2 2 SOURCE ROTOR VANE MOTOR DEVICE BACKGROUNDOF THE INVENTION:

1. Field of the Invention:

This invention relates to motors. More particularly, it relates toeccentric rotor, concentric vane type motors for delivering power by wayof an output shaft in response to flow of a working fluid therethrough.

2. Description of the Prior Art:

A wide variety of types of motors have been employed in the prior art.Included are motors which delivered power in response to flow of aworking fluid therethrough, the working fluid flowing from a highpressure to a lower pressure. These motors have employed compressibleworking fluids and have employed incompressible working fluids. With theincreasing concern for improving the quality of our environment,conventional internal combustion prime movers are looked upon withdisfavor and interest in other motor systems has been generated. Typicalof one such low entropy engine and system is U. 8. Pat. No. 3,479,817,Wallace L. Minto. The Rankine cycle has been used in steam generatingplants, on ships and nuclear submarines and the like, but prior artattempts to make use of the Rankine cycle in many applications, such asfor replacing an internal combustion engine in the automobile, have notproven engineeringly and economically feasible. For example the Rankinecycle inherently has an efficiency of only about 8-20 percent when usedwith low entropy fluids in an external combustion system. Where athrottle is employed, there are efficiency losses that reduce thisefficiency by up to 50 percent. Also, the prior art motors which couldbe employed in such a system had severe disadvantages and, insofar as Iam aware, no machine employing the Rankine cycle has ever achieved itsoptimum potential. For example, a 200 horsepower steam engine ofconventional reciprocating piston design would weigh about two tons. Onthe other hand, a steam engine turbine which would be feasible wouldhave a high rotational speed of 20,000-30,000 revolutions per minute(rpm) and would require a very expensive transmission to come down intothe range of useful rotational speeds and adequate torque. Moreover,such high speed steam turbines were damaged by droplets of water and hadto be operated entirely in the vapor region with care being taken thatthe steam did not become wet," or contain droplets of water.

Specifically, the prior art motors have not provided a motor devicehaving one or more of the following desirable features: (1) an improvedmotor with operating characteristics allowing over-all systemefficiencies and performance for a compressible working fluid flowingtherethrough that provide broad application potential for the Rankinecycle external combustion system; (2) a compressible fluid motor havingmost of the desirable characteristics of both the piston motor and theexpansion turbine, while alleviating problems caused by the limitationsassociated with these units; (3) a compressible fluid motor whichobviates the need for a reducing throttle valve as a part of an externalcombustion system and alleviates the problem with system efficiencylosses from throttling that have been inherent in such compressiblefluid systems, such as the Rankine cycle engines; (4) an expansiblefluid motor capable of exhausting at or near a low receiver pressure,such as condenser pressure, throughout most of the range of operatingcondition, thereby substantially reducing exhausting losses inherentlycaused by over-expansion or by under-expansion of the working fluidduring the expansion work cycle; (5) an expansible fluid motor that isinternally reversible and that has torque capabilities allowing its useto drive mobile equipment; directly and efficiently, without requiringthe use of a transmission, incorporating variable ratio and reversinggears and a clutch; (6) an expansible fluid motor capable of exhaustingsubstantial amounts of liquid condensate with the working fluids withoutadverse effects on the motor such that the motor can operate in eitherthe thermodynamic superheat region of the working fluid, in thesaturated region, or from the superheat region into the saturatedregion, for much greater flexibility and power delivery capabilitieswith a given working fluid; (7) a motor having a very great mass rate offlow of working fluid therethrough at moderate rotating speeds such thatit can deliver very high torque and power levels for its size; (8) anexpansible fluid motor which may be supercharged by increasing the inletvolume per revolution beyond the capability of the adjustable exhaustcontrol to exhaust the fluid at the exhaust receiver pressure such thatthe lowest pressure internally of the exhaust control is greater thanthe exhaust receiver pressure for effecting great increases in bothtorque and power instantly at any operating speed; (9) compressiblefluid motors that are operable on a wide variety of fluids; and,specifically, motors that are useful with fluids from naturallyoccurring high pressure sources, such as geothermal wells, and exhaustinto ambient low pressure receiver means, such as the atmosphere; andthat have structures that enable delivering large quantities of power atthese naturally-occurring pressures without intolerable vibrations, sizeand cost; and (10) compressible fluid motors that, though superficiallysimilar to prior art motors, are really quite different and takeadvantage of double effects, as described in more detail in the Theory"section later hereinafter, for far greater power and torque outputs thanhave been possible heretofore with comparably sized motors.

BRIEF DESCRIPTION OF THE DRAWINGS:

FIG. 1 is a front elevational view of a motor in accordance with oneembodiment of this invention.

FIG. 2 is a side elevational view of the motor of FIG. 1.

FIG. 3 is an enlarged cross sectional view taken along the lines III-IIIin FIG. 2.

FIG. 4 is an enlarged sectional view taken along the lines lV-IV in FIG.1, with its torque control sleeve shown in a position to effect deliveryof high torque.

FIG. 5 is an enlarged sectional view taken along the lines IV-IV in FIG.1, with the torque control sleeve shown in the cut-off, or zero torque,condition.

FIG. 6 is an enlarged sectional view taken along the lines lV-IV in FIG.1, with the torque control sleeve in a position for effecting low torquedelivery.

FIG. 7 is a perspective view of the vane axle pin and one of the vanesof the motor of FIG. 1.

FIG. 8 is a partial cross sectional view taken along the lines VIII-VIIIin FIG. 1, partially cut away to show an exhaust, or discharge, ringpositioned for late, or retarded, exhausting, or discharging, of theworking fluid for effecting maximum internal expansion thereof duringforward rotation of the motor.

FIG. 9 is a partial cross sectional view taken along the lines VIIlVlIIin FIG. 1, broken away and partly in section to illustrate an exhaustring in a position to effect early, or advanced, exhausting of theworking fluid, effecting minimal internal expansion thereof.

FIG. 10 is an exploded isometric view of a motor in accordance withanother embodiment of this invention.

FIG. 11 is a partial cross sectional view of an assembled motor, withthe rotor and vanes removed, in accordance with the embodiment of FIG.10, illustrating the torque control sleeve in the shut-off, or zero,torque setting for reverse direction of rotation.

FIG. 12 is a schematic view, partly in section, illustrating a system,including a reversing valve in position for effecting forward directionof rotation of a motor, in accordance with another embodiment of thisinvention.

FIG. 13 is a partial schematic view, partly in section. of theembodiment of FIG. 12, illustrating the reversing valve in a positionfor effecting reverse rotation of the motor.

FIG. 14 is a partial schematic illustration, partly in section, showingthe reversing valve in the off position.

FIG. 15 is a partial end view showing one exhaust ring in the retardedposition for effecting maximum internal expansion of the working fluidin the forward direction of rotation of the motor of FIG. 10.

FIG. 16 is a partial cross end view showing the exhaust ring of theembodiment of FIG. 15 in the advanced position for effecting minimuminternal expansion of the working fluid.

FIG. 17 is a partial end view showing the exhaust ring in the reverseposition for effecting operation ofthe engine in the reverse directionof rotation.

FIG. 18 is a cross sectional end view of a housing of the embodiment ofFIG. 10.

FIG. 19 is a partial cross sectional end view illustrating a vane tip,seal, and internal surface of a torque control sleeve in accordance witha specific embodiment of this invention.

FIG. 20 is a partial end view ofa conventional motor of the prior art.

DESCRIPTION OF PREFERRED EMBODIMENTS:

It is a primary object of this invention to provide an eccentric rotor,concentric vane device that obviates the disadvantages of the prior artdevices and has one or more of the desirable features delineatedhereinbefore and not heretofore provided by the prior art.

It is also an object of this invention to provide an eccentric rotor,concentric vane device having combined selective ones of the desirablefeatures, including particularly feature (10), for effecting optimumoperation in a given application of the motor.

It is another object of this invention to provide a system employing aneccentric rotor, concentric vane motor device having all of thedesirable features delineated hereinbefore.

It is another object of this invention to provide an eccentric rotor,concentric vane motor device having specific improved structure inaccordance with the respective embodiments delineated and describedhereinafter and taken in conjunction with the accompanying drawings.

Referring now to the figures, and particularly FIGS. 1-9, there isillustrated one embodiment of this invention in the form of a motor 11,or eccentric rotor, concentric vane motor device. The motor 11 comprisesa stator 13, a rotor, or rotor assembly, 15, FIG. 3, and a vane assembly17.

The stator 13 includes a main body member 19 having a base or mountingbracket 21, FIGS. 1 and 2. Main body member 19 has peripherally disposedcircular flanges 23, FIG. 3, that extend longitudinally for affixingends, or cap members, 25 and 27. A longitudinal cylindrical cavity 29 isformed in the inner face of the main body member 19 and includes a mainchamber. An inlet port 31, FIG. 4, is formed in the inner face of bodymember 19 and extends from the medial top, or 0, position thereof forabout clockwise. The inlet port 31 has its leading and trailing edges 35and 33 extending longitudinally for the full length of the body member19 for providing a maximum flow area. The inlet port 31 communicates viapassageway 37 in body member 19 with an internally threaded, integrallyformed collar 39 to facilitate connecting an inlet of motor 11 with ahigh pressure source of working fluid, which will be described in moredetail later hereinafter. Similarly formed in the inner face of the bodymember 19 is an exhaust, or discharge, port 41. The discharge port 41has a leading edge 43 that extends longitudinally of the longitudinalcylindrical cavity 29 and body member 19, and that is spaced about 25peripherally thereof from the trailing edge 33 of the inlet port 31. Thedischarge port 41 also has a trailing edge 45 that extendslongitudinally of the longitudinal cylindrical cavity 29 and trails theleading edge 43 approximately 90. The discharge port 41 communicates bya passageway 47 in body member 19 with an internally threaded,integrally formed collar 48 to facilitate connection with a low pressurereceiver that will be described in more detail later hereinafter.

A pair of cap members 25 and 27, FIG. 3, are affixed to opposite sidesof the body member 19. Each cap member includes a curved conicalperipheral wall 49 whose outer border abuts the outer face of arespective flange 23 and is secured thereto by bolts, or cap screws 51,engaging aligned bores in the respective cap member and tapped bores inthe flanges 23. Coaxial bearing sleeves 53 and 55 are integrally formedwith the cap member 25 and 27. A thrust plate 57 is secured to thebearing sleeve 55 by cap screws 59, with a suitable seal 61 sandwichedtherebetween. A coaxial collar 63 is secured by cap screws 65 to theouter end of bearing sleeve 53. The coaxial collar 63 is disposed abouta shaft extending therethrough and contains a suitable shaft seal 67.Suitable bearings are interposed intermediate the bearing sleeves andtheir respective shafts. The bearings will be appropriate to the use inwhich the motor device is being employed. As illustrated, rollerbearings 69 are employed.

The end caps also define exhaust, or discharge, chambers 71. The curvedperipheral walls 49 contain an internally threaded aperture 73 tofacilitate connecting, as by threaded conduit, the discharge chamber 71with the low pressure receiver.

The rotor assembly 15 includes a pair of opposite and mating circularplates 75 and 77 that rotatably engage, or proximate, the circularapertures 79 and 81 in annularly disposed plates 83 and 85. If desired,bearing materials can be provided at the interface between therespective circular plates 75 and 77 and the inner walls of apertures 79and 81. The follower means, such as the vane guides 87, are retainedintermediate the oppositely disposed faces of the circular plates 75 and77. The vane guides 87 serve as both pistons and means forinterdigitating the vanes, thereby effecting a change in volume ofsubchambers intermediate the respective adjacent vanes as the rotorassembly and the vanes are rotated within the main chamber. Eachsubchamber 88, FIGS. 3 and 4, is defined by a pair of confronting vanefaces on its sides. by a vane guide and an interior surface 117 of thetorque control sleeve 119 at its inner and outer boundaries, and theannular plates 83 and 85 at its ends. Each subchamber 88 varies from aminimum volume at the outermost, or 0, position of the vane guide to amaximum at the innermost, or 180, position of the vane guide 87. Thevane guides 87 traverse inwardly and outwardly radially along theadjacent vanes to effect the improved seal that makes practical thisinvention, as described with respect to the vanes and the vane assemblylater hereinafter.

Each of the illustrated follower means comprises a vane guide 87 thatextends longitudinally along the rotor with vane engaging surfaces oneach side that are disposed symmetrically about a central axis thereof.Each of the vane engaging surfaces of a vane guide 87 has the samepredetermined radius of curvature with respect to the central axis. Asillustrated, each vane guide 87 comprises a cylindrical roller 89,rotatably mounted on a shaft 91. Rotation of the cylindrical roller 89is facilitated by suitable bearing means, such as insert 93. Each shaft91 is fixed between shoulders 95 of the circular plates 75 and 77 by capscrews 97 penetrating through apertures 99 in the circular plates 75 and77. v;

One of the advantages of this invention is that the improved structureof the vane guides 87 make possible employing at least 8 vanes in thevane assembly, and 8 vane guides 87, whereas the prior art structureswere limited to a lesser number and were, consequently, less efficientand had significant disadvantages, as indicated hereinbefore. 1n theembodiment illustrated, vane guides 87 are employed.

A power shaft 101 is fixed to and extends coaxially from the circularplate 75 through roller bearing 69 in the bearing sleeve 53. Asindicated hereinbefore, it is journalled within coaxial collar 63 andshaft seal 67 and extends outwardly to deliver the power, as by way ofsuitable coupling means. to using apparatus.

The coupling means may be any of the conventional coupling means,including but not limited to linear, inline couplers, gear reducingcouplers, or properly sized sheaves and endless member drives; such as,belts or chains. As in conventional practice, one end of the couplingmeans will be connected with the shaft 101; as by a key and slotcombination, or splines (not shown). A second shaft 103 extendscoaxially from the circular plate 77 and is journalled for rotationalmovement in roller bearings 69 in bearing sleeve 55, to provideadditional support to the rotor assembly.

As illustrated, each .of the shafts 101 and 103 has a male threadedportion 105 threadedly engaging a tapped aperture in the respectivecircular plates 75 and 77. The portion 105 pulls the respectiveshoulders 107 into tight engagement with the respective circular plates75 and 77 to form a strong connection therebetween. The threads areformed such that they are not loosened in normal rotation. A set ofroller thrust bearings 109 are prvided intermediate the exterior of eachrespective circular plate and 77 and its adjacent end caps 25 and 27.The thrust bearings 109 may be countersunk to keep the clearanceintermediate the plates to a minimum. Preferably, aircraft type rollerbearings are employed as the thrust bearings 109, although otherbearings may be employed as appropriate to the use of the motor device.The bearings 109 provide improved structure and should not be omittedcasually.

The rotor assembly 15 is eccentrically disposed within the longitudinalcavity 29, and its power shaft 101 is eccentric with respect to thecentral axis of the longitudinal cavity 29.

The vane assembly 17 is located in a vane assembly cavity 121 that isdefined by sleeve 119, FIG. 4, concentrically within the longitudinalcavity 29; and, as depicted in FIGS. 3, 4 and 7, includes a floatingaxle pin 111 that is substantially coaxial with the cylindrical cavity29 and that extends between the circular plates 75 and 77. A pluralityof vanes 113 extend radially outwardly from the axle pin 111 and areindividually pivotal thereon. As illustrated. each vane is provided witha curvd end face 115 of substantially the same radius of curvature asthe inside wall 117 of the sleeve 119. The curved end face 115 of eachvane 113 is in substantial sliding engagement with the sleeve 119 suchthat it forms a satisfactory seal for confining the fluid in therespective subchambers on either side thereof. The seals intermediatethe vanes 113 and the sleeve 119 have not been particularly criticalbecause the differential pressure between adjacent subchambers is notinordinately high and because the centrifugal force on the vanes tendsto retain sufficient sealing engagement between the respective vane ends115 and the sleeve 119. Any type of seal appropriate to the use may beemployed, another of which will be illustrated and describedspecifically later hereinafter.

As illustrated in FIG. 7, each of the vanes 113 have integrally formedwith the inner radial end thereof at least one annular knuckle thatconformingly engages the axle pin 111. The knuckles 125 of respectivevanes 113 are axially offset relative to each other along the axle pin111 and are stacked on the axle pin 111 with their confronting faces insliding engagement to permit the relative interdigitating, or rocking,of the vanes 113 about the axle pin 111. It will be appreciated, and asspecifically illustrated in my co-pending application entitled RotaryVane Device," filed even date herewith, the vane with a central knucklehas a knuckle that is twice as wide as ordinary and disposedintermediate the adjacent knuckles on either side. If desired, the vanesmay have their respective knuckles disposed at one-half of the axle pin11 1 plus the thickness of one knuckle and intermesh such that the useof the wide central knuckle is obviated. Any other method of supportingthe vanes that will allow the interdigitating thereof may be employed.Since the vanes are accelerated and decelerated during rotation,however, symmetrical arrangement of the knuckles with respect to atransverse plane through the vane's center is preferable.

The respective vanes 113 have lateral faces 127 that are concavedinwardly toward the central plane of the vane such that the respectivefollowers, or vane guides, 87 are maintained in substantially uniformsealing engagement with the vane lateral faces 127 as the vane" guides87 traverse radially inwardly and outwardly therealong during rotationof the rotor assembly 15. By substantially uniform sealing engagement ismeant an engagement such that a satisfactory seal is maintainedintermediate the respective vane guides 87 and the vanes 113 so that thevane guides 87 can serve as pistons as well as interdigitating means asthey traverse radially inwardly and outwardly along the respective vanes113. As is well recognized, what is satisfactory sealing engagement willvary depending upon the application, or use; which determines severalfactors. These factors include the size of the unit, the differentialpressure across a vane guide 87 from the subchamber to the interior ofthe rotor assembly 15, the total pressure of the fluid being handled inthe subchamber and the emciency desired. To illustrate, I have foundthat as much as 0.0l inch clearance may be tolerated between the vaneguides 87 and the vane lateral faces 127 with large motors such as maybe employed with low pressure steam. For example, with the low pressuresteam that may be emitted from geothermal wells, the motor device mayhave dimensions as large as 30 inches in length by 36 inches indiameter; or larger, if used on individual steam wells. On the otherhand, when employing the motor with low entropy fluids flowingtherethrough, I have found it preferable that a clearance of less than0.005 inch; for example, about 0.001-0.003 inch; be employed between thesurface of the vane guide 87 and the vane lateral faces 127. The lattermotors may be only about 4 inches in length and 6 inches in diameter,yet develop enough power to operate a small automobile.

The improved seal means described hereinbefore makes practical theeccentric rotor, concentric vane motor device of this invention aftermany years of unsuccessful attempts by the prior art to employ similardevices on a commercial scale. The preferred embodiment employs rollersfor vane guides to make use of rolling friction for low even wear.Consequently. the improved seal means is durable and trouble-free, theroller vane guides rolling along the concave vane face. I have attemptedto delineate, through mathematical experts and computer computations,the exact definition of the concavity of the surface of the lateralfaces 127 but have not been successful to date. The concavity can bedelineated graphically, employing a scale that is larger than actualsize. I have developed an empirical formula by trigonometry that isclose, also. In practice, I have found exact mathematical delineation tobe unnecessary. Instead, I employ a grinding jig with grinding rollersto duplicate the physical relationships and dimensions employed in themotor device 11. Specifically, the grinding of the vane faces iseffected by repeatedly moving the vanes and sized grinding rollersthrough 360 as the vanes would be moved by the rotor assembly withincreasing distances of eccentricity, up to the eccentricity actuallyemployed in the motor device 11. By increasing distances of eccentricityis meant the increasing moving apart, with successive revolutions, ofthe shaft of the vane axle pin 111 and the axis of the shaft of thegrinder rollers that is equivalent to the axis of the shafts 101 and 103of the rotor assembly 15. In this way, I get exact initial engagementand do not have to worry about the clearance. Once a particular vanecontour, or concavity, has been established for a particular motor, itmay be reproduced by conventional methods of copying.

An integral and adjustable flow through and torque control means forcontrolling torque output is provided for the motor 11 so that it may beoperated without requiring a throttle and the throttle-caused losses inefficiency. As illustrated, the flow through and torque control meanscomprises a torque control sleeve 119, referred to hereinbefore assimply sleeve, conformingly disposed interiorly of the longitudinalcylindrical cavity 29. Specifically, the sleeve 119 mates and telescopeswithin the cavity 29 and rotatably and slidably engages the inside faceof the cavity 29 to permit angular adjustment of the torque controlsleeve 119. The torque control sleeve 119 has at least an inlet aperturein the form of a first set of longitudinally extending inlet slots 131,FIG. 4. The inlet slots 131 communicate between the interior of the vaneassembly cavity 121, and the inlet port 31, FIG. 4. The set of inletslots 131 extends circumferentially around the torque control sleeve 119for about the same circumferential distance as that of the inlet port31. The inlet slots 131 may be inclined in an inward cockwise directionto direct the inlet gas against the leading vanes for preserving theenergy of the velocity component of flow. Advancing the torque controlsleeve in a first direction will increase the effective flow areathrough the inlet aperture and inlet port until the inlet aperture is ata maximum, as illustrated in FIG. 4. On the other hand, the torquecontrol sleeve 119 may be retarded, or rotated in a second directionopposite the first direction, to decrease the effective flow areathrough the inlet aperture and inlet port 31. The degree of retardationmay be sufficient to completely close off the inlet port, as illustratedin FIG. 5; or to effect a reduced flow of fluid through the motor 11, asillustrated in FIG. 6.

The flow through and torque control means also includes a means 133 foradvancing and retarding the torque control sleeve. As illustrated, themeans 133 for advancing and retarding the torque control sleeve includesa gear tooth rack 135, FIG. 5, formed in the outer periphery of thesleeve 119 and a pinion gear 137. The pinion gear 137 is housed in agear housing cavity 139 that is formed in the inner face of the bodymember 19 shortly above the base 21. The pinion gear 137 is fixedlymounted on a shaft 141 journalled in a wall of the housing cavity 139and having a knob 143 fixed thereto to permit its rotation in angularlyadjusting torque control sleeve 119.

The flow through and torque control means also includes a discharge flowcontrol means for controlling the volumetric rate of flow of fluidthrough the discharge ports of motor 11 such that the pressureinteriorly of the vane assembly cavity 121, in the main chamber, orcavity, 29 can be controlled to reduce losses from over-expansion andunder-expansion of a working fluid flowing therethrough. Specifically,the discharge flow control means includes a torque control sleeve havingat least one discharge aperture communicating between the vane assemblycavity 121 and the discharge port 41. As illustrated, the torque controlsleeve 119 has a second set of exhaust, or discharge, slots 147 formedtherein for exhausting fluid from the vane assembly cavity 121 to thedischarge port 41. The second set of discharge slots 147 extendcircumferentially around the torque control sleeve 1 19 such that theyare moved in the same rotational direction as are the inlet slots 131.The discharge slots 147 are disposed so closely adjacent the inlet slots131, however, that there is communication between the discharge port 41and the vane assembly cavity 121 even when the inlet slots 131 have beenmoved into the cut-off position as illustrated in FIG. 5. Moreover, theadvancing and retarding of the discharge slots 147 is relativelyinconsequential to the effect on the torque control of the motor 11,since the primary control is effected by the inlet slots 131,illustrated in FIG. 6.

If desired, a plurality of torque control sleeves may be employed, oneeach for the inlet aperture and the discharge aperture such that therespective effective flow areas of the apertures may be controlledindependently. Ordinarily, such independent control is not necessary,and it is sufficient to control the flow through and torque bycontrolling the effective flow area of the inlet aperture.

As illustrated, the discharge flow control means also includes at leastone angularly adjustable exhaust ring 149, FIGS. 8 and 9, disposed at atleast one end of the main chamber 29. The exhaust ring 149 has at leastone discharge aperture communicating between a discharge port such asthe interiorly threaded aperture 73 in the cap member 25 and the vaneassembly cavity 121. The exhaust ring 149 is angularly adjustable, orrotatable, for advancing or retarding exhaust of the working fluidflowing through the motor 11. Rotating the exhaust ring in a firstdirection to a position illustrated in FIG. 9, will initiate thedischarge flow of the working fluid from the respective subchambersearlier in a revolution of the subchamber, effecting minimal expansionof the working fluid in the motor 11. Moving the exhaust ring 149 in theopposite direction, as illustrated in FIG. 8, will effect a laterdischarge of the working fluid from the respective subchambers during arevolution of each respective subchamber and effect a maximum expansionof the working fluid in the motor 11. Specifically, the angularlyadjustable annular exhaust rings 149, previously designated as annularplates 83 and 85, are provided at each end of the main chamber forincreasing the flow of the working fluid from the respective subchambersduring the discharge portion of a revolution of each subchamber. Theangularly adjustable annular exhaust rings 149 are coaxial with the mainbody member 19, rotatably engaging the opposite end faces of the bodymember 19 with the peripheral surfaces of the exhaust rings 149 engagingseals, such as O-rings 151, FIG. 3, disposed interiorly of the flanges23.

As illustrated, the discharge aperture comprises a set of a plurality ofcircumferentially spaced discharge slots, or apertures, 153 that extendabout 100 around the exhaust ring 149. Each of the slots 153 has itsinner end positioned proximate the circular apertures 79 and 81 andextends radially outwardly. The discharge slots 153 are more elongatewhere they initiate discharge of the fluid from the vane assembly cavity121, and grow progressively smaller, or less elongate, commensurate withthe radial dimensions of the subchamber at respective positions withinthe vane assembly cavity 121 exteriorly of the rotor assembly 15, as canbe seen in FIGS. 4-6.

The discharge flow control means also includes means 155, FIG. 9, foradvancing and retarding the exhaust rings 149; the means 133 foradvancing and retarding the torque control sleeve 119 having beendescribed hereinbefore. The means 155 for advancing and retarding theexhaust ring comprises a gear tooth rack 157 disposed about the outerperiphery of each exhaust ring 149, and a pinion gear 159. The piniongear 159 is disposed in the gear housing cavity 161 and supported onshaft 163. The shaft 163 is fixedly connected with the pinion gear 159and with knob 165 to facilitate advancing and retarding the exhaust ring149 exteriorly of the motor 11. The gear tooth rack 157 extends aroundthe exhaust ring 149 for the requisite distance to effect the desiredadvancing and retarding of the discharge slots 153. As illustrated, itextendsabout 45 circumferentially of the exhaust ring 149.

Each of the annular plates 83 and have their respective gear tooth racks157, pinion gear 159, and gear housing cavity 161. Preferably, however,a single knob and a single shaft 163 suffice to advance and retard therespective annular plates 83 and 85 concurrently for effecting thedesired position. As illustrated, the trailing slot 153a of the slots153 may vary from the advanced position of about 160, FIG. 9, to theretarded position of about 205, FIG. 8, measured clockwise from the 0position of the vane assembly cavity 121.

In operation of the motor 11, each subchamber 88 intermediate theopposed faces of the vanes are rotated through 360. At the topmost, orzero, position, the subchamber 88 has a minimum volume, since thefollower means 87 therein substantially engages the face of the torquecontrol sleeve 119. On the other hand, each respective subchamberobtains its maximum volume at the 180 position with its respectivefollower means 87 being closest to the axle pin 111, and the adjacentvane faces 127 being at their maximum spread. It is noteworthy that thesum of the volume expansions of the subchambers 88 during a singlerotation of the rotor exceeds the total volume of the longitudinalcylindrical cavity 29. The inlet port 31 communicates with a source ofpressurized fluid, preferably an expansible fluid for the motorillustrated. For example, steam, a low entropy fluid vapor likethiophene, or other gas may be employed. The exhaust port 41 isconnected to a low pressure receiver. The low pressure receiver maycomprise the atmosphere if the high pressure fluid is an economicalfluid such as steam from a geothermal well; or it may comprise acondenser in a system having a recirculation means and employing a lowentropy fluid. The internally threaded aperture 73, forming a dischargeaperture for the discharge chamber 71 will also communicate with the lowpressure receiver. The distance between the outer opposed lateral faces127 of adjacent vanes 113 at a 0 position of a subchamber is less thanthe distance between the trailing edge 33 of the inlet port 31 and theleading edge 43 of the discharge port 41.

The high energy fluid enters successive subchambers of reduced volume,beginning near their top, or 0, positions and continuing until they passthe inlet cut-off point as defined by the last inlet slot 131 at theinlet port 31. It is believed instructive to interrupt the operationaldescription at this point to consider the theory of operation. Thistheoretical discussion is given, not in limitation, but in explanationof why this invention is so surprisingly superior to, and howdramatically this invention departs from, the superficially similarprior art fluid motors.

THEORY The motor 11 develops its power by taking advantage of both oftwo important effects( 1) converting a differential force on the vanesinto torque and (2) a pseudo cranking action analogous to that of aconventional reciprocating engine.

The conventional differential force on the vanes works as follows, thedescription being given with respect to prior art devices, asillustrated in FIG. 20. Therein, the radial distance D, is less than theradial distance D therefore, the respective areas have the samerelationship and the force F, is less than the force F,. Also the radialdistance D, is substantially equal to the radial distance D andtherefore their areas are about equal. Since the pressure P is greaterthan the pressure P the force F; is greater than the force F;,.Consequently torque is imparted to the vanes and thence to the rotorassembly and to its output shaft 101.

It is noteworthy that the differential forces on the outer radialportion of the vane contributes to an unbalanced cantilever force on thevane, the force such as 1" acting about the fulcrum C,, or the axis ofthe prior art pivotal support of the vane by the rotor assembly. Theseunbalanced cantilever forces, in turn, cause excessive forces F 4 whicheffect offsetting force against the tips of succeeding vanes,illustrated as F In the case of a floating vane axle, these unbalancedcantilever forces are detrimental to performance of the motor. Theunbalanced cantilever forces are much less in this invention than in theprior art motors, since the product of the pressure times the area onthe respective opposed faces of a particular vane are more nearly equalthan in the prior art. Consider, for example, FIG. 6. As the pressure P;in a subchamber 88 decreases, the area A, on which it acts increases.compared to the area A on which the higher pressure P, acts, lesseningthe unbalanced cantilever force on that particular vane and theresultant force on the following vane tip. Thus, improved performance iseffected.

The major forces effecting rotational torque in motor 11 are, however,due to the pseudo cranking action, which is effected as follows. Thepressure forces exerted on the peripheral wall 117 of the torque controlsleeve 119 and on the vane guides 87, serving as a piston, force thesesurfaces apart and act about two centers, one center being the center ofthe vane axle 111, and the other being the center of the rotor assembly15; and provides, in essence, a mechanical cranking action similar tothat of a conventional reciprocating piston engine. Expressed otherwise,the pressures P P P P, in the respective subchambers 88, FIG. 6, act onthe respective vane guides 87 having a moment arm with respect to thecentral axis C of the rotor assembly 15 to impart torque to the outputshaft 101. The torque output is then converted to useful work. Thiseffect represents a dramatic departure from the superficially similarprior art type fluid motors. Effecting most of the torque force in thismanner also relieves the vanes of much of the unbalanced cantilever typeforces described hereinbefore.

Moreover, this pseudo cranking action and the use of a large number ofsubchambers illustrates the advantage of incorporating a relativelylarger number of vanes into the motor 11 than the prior art to minimizethe pressure differential between the adjacent subchambers, thereforefurther reducing the unbalanced cantilever forces on the vanes.

It is also noteworthy that the torque and power control are regulated,not by flow restriction of the inlet openings in the torque control ring1 19, but by governing the size, or volume of the subchamber presentedfor loading at full inlet pressure, prior to the beginning of theexpansion. The expansion occurs after the cut-off point; that is, afterthe trailing vane of a subchamber passes the last of the inlet openings,or inlet apertures, in the torque control sleeve 119. Three types ofwork are involved in the vapor motor as follows:

where:

W, total work W inlet work W work of expansion, and

W the negative work spent exhausting the fluid. The inlet work isdefined by the following equation:

hile! where:

P inlet pressure. and

AV= the differential volume expanding the volume of the subchamber from0 to the maximum inlet volume. The inlet work is a major factor astorque level increases, especially in supercharged operation. The workof expansion is the usual thermodynamic work property of a working fluidas follows:

exp M where pressure and volume are used in a usual thermodynamic sensebetween the inlet and discharge apertures. The negative work ofexhausting is similar to the inlet work and is a function of the productof the pressure times the volume, where the pressure is the receiverpressure, even in the supercharged operation.

in supercharged operation, the fluid at the pressure above the receiverpressure expels itself simultaneously from the point of opening of theexhaust apertures until it reaches receiver pressure. The motor mustthen expel the remainder against receiver pressure only.

As will become apparent from the continued operational description, thepositioning of the exhaust rings is done to effect initiation of theexhausting phase at the point where the expanded fluid in the respectivesubchamber is equal to the receiver pressure, unless operating in asupercharged condition. The exhaust openings are not restricted as ameans of controlling the exhaust pressure.

In low torque level operations, a given subchamber is loaded with anamount of fluid to give the desired torque. The fluid is expanded in thesubchamber until the pressure therewithin is substantially equal to thereceiver pressure. At that point the exhaust, or discharge, ports areopened such that there is no lost work through either under-expansion orover-expansion of the fluid, defined hereinafter.

At high torque levels, the respective subchamber is loaded with anamount of fluid to give the torque desired. The fluid is expanded toequal the pressure of the receiver. To effect this result, the dischargeports are angularly positioned to initiate exhaust; for example, throughthe suitably positioned torque rings and the discharge apertures in thetorque control ring; much later than that for low torque operation.

In supercharged operation, the inlet area is so large that it isimpossible to discharge all the fluid through the exhaust apertures atreceiver pressure. The expansion is a maximum in the external combustionengine and it is expanded until the physical point at whichrecompression would begin again if the fluid were not exhausted. Theexhaust of the fluids is thus begun to prevent recompression. Thepressure in the subchamber would still be greater than the receiverpressure in the supercharged operating condition.

These theoretical and operational considerations may assist inunderstanding the routine operational description hereinafter.

CONTINUED ROUTINE OPERATIONAL DESCRIPTION When m respective subchambersreach the initial discharge slots 153, the fluid begins exhausting tothe low pressure receiver. The position of the initial discharge slot153a is adjusted by rotating the exhaust rings 149 so that at the pointexhausting may begin, the pressure inside the subchamber approximatesthe pressure existing in the low pressure receiver. This results in theminimum work being required to expel the expanded fluid from the motoras the exhausting chamber rotates further and contracts until it againreaches the position. The fluid also exhausts through discharge slots147 in torque control sleeve 119. The torque and power output of theengine is varied by angularly adjusting the torque control sleeve. Thetorque is increased with the advance of the torque control sleeve 119clockwise to its maximum, as illustrated in FIG. 4. The torque controlsleeve 1 19 is rotated counter clockwise to effect a shut-off position,FIG. 5, or a lesser torque, FIG. 6. At low torque operations it may bedesirable to advance the cut-in point of the discharge slots 153 byrotating the exhaust ring 149 to the position illustrated in FIG. 9.Expressed otherwise, the exhaust rings 149 may be rotated within theirlimits to'position the discharge slots 153 so that over-expansion of theworking fluid is avoided (expansion to a pressure level below that ofthe low pressure receiver); or so that under-expansion of the workingfluid is avoided (exhausting at a pressure in excess of that of the lowpressure receiver).

One advantage of the motor 11 described hereinbefore is that it may beoperated at supercharged conditions. Supercharging is effected byadvancing the torque control sleeve 119 to a setting of the inletaperture of such great volumetric flow capacity that the flow capacityof the limiting position of the exhaust ring adjustments is surpassed atthe pressure of the low pressure receiver; with the discharge slots 153at their most retarded position, as illustrated in FIG. 8, correspondingto a position where exhausting is required to prevent recompression ofthe fluid in the subchambers. Consequently, pressures interiorly of themotor become greater than that of the low pressure receiver, such thatthe pressure within the respective subchambers is appreciably above thatof the low pressure receiver, referred to as a supercharged condition.Substantial increases in torque and power can be effected in thesupercharged condition over normal operating ranges employing controlledexpansion, because of the greater inlet displacement work performed andthe high pressure existing during the expansion cycle. Duringsupercharging, some working fluid exhaust superheat is increased, andreduction in over-all system efficiency is experienced; but thecapability of instantly gaining up to 50 percent in excess of design inboth power and torque at virtually any operating speed offers verysignificant advantages in many applications for which the motor 11 maybe employed. Expressed otherwise, the motor 11 has an inlet aperturethat defines with inlet port 31 a first flow area in or near the wideopen position that is sufficiently large that more of the working fluidat the pressure exteriorly of the inlet aperturecan flow through thefirst flow area into the subchambers within the vane assembly cavity 121than can flow through a second flow area, representing the totaldischarge flow area from the vane assembly cavity 121, at the pressureexteriorly of the discharge apertures such that internal pressureincreases and supercharged operation of the device is effected forgreater power output.

ANOTHER EMBODIMENT:

Another embodiment of the invention is illustrated, in exploded view, inFIG. 10. Therein, the motor 11 comprises the stator 13, rotor assembly15, and vane assembly 17, as described hereinbefore. The motor 11 ofFIG. 10, however, represents an embodiment such as might be employedwith low pressure steam from geothermal steam wells and is structurallydesigned for larger sizes and more rugged service than the embodimentdescribed hereinbefore.

The stator 13 has the same functional apertures, elements, chambers andthe like described hereinbefore, In the embodiment of FIG. 10, however,the stator 13 contains a passageway 171 through which the output shaft191 passes and serves as the body to which the end housings, or capmembers, 25 and 27 are attached. The cap members 25 and 27 may beattached as described hereinbefore or by means of mounting bracketsattached to the stator 13, to the cap members, or both. The cap members25 and 27 provide respective recesses 173 for receiving the torquetransmission and output gears 175 and 177 which will be discussed inmore detail with respect to the power output shaft 101 laterhereinafter. The recesses also serve as the exhaust, or discharge,chamber 71 with the internally threaded aperture 73 to facilitateconnection with a low pressure receiver. The cap members 25 and 27 alsoprovide bearing pedestals 179 that support and position both the vaneassembly 17 and the rotor assembly 15, as will become apparenthereinafter.

The rotor, or rotor assembly, 15 has the same elements as describedhereinbefore. For example, the vane guides 87 are constructed andsupported intermediate the circular plates 75a and 77a as describedhereinbefore. Instead of having the power delivery and support shaftsscrewed into the circular plates 75a and 77a for support, however, thecircular plates 75a and 77a are mounted via bearings 180 on the bearingpedestals 179 in cap members 25 and 27. Thrust bearings 183 are disposedintermediate the rotor assembly 15 and the cap members 25 and 27 toretain the rotor assembly 15 against axial movement. Each of thecircular plates 75a and 77a contain a cylindrical extension 185 that isfixedly engaged with a torque output gear 177. By fixedly engaged" ismeant only they rotate in unison without slippage. Any conventionalmeans of preventing slippage between the cylindrical extension 185 andthe torque output gear 177 may be employed. A conventional slot and keyarrangement 189 is illustrated.

The torque output gears 177 run in mesh with torque transmission gears175 that are fixedly engaged with the output shaft 101. Specifically,the output shaft 101 is fixedly engaged with an outer shaft 191 that isalso fixedly retained in engagement with the torque transmission gears175, as by meshing splines, to facilitate assembly. Thus, the outertubular shaft 191 is journalled in the passageway 171 to provide a pointof support for the power output shaft 101 which, because it is moreelongate than in the embodiment described hereinbefore, would otherwisebe subject to flexure. The torque transmission gears 175 are disposed atrelatively widely spaced points along the output shaft 101 in order tomake the power input more nearly uniform along the shaft and preventflexure. also. The power output shaft 101 is also supported adjacenteach end by way of shaft bearings 193 and journalled in shaft seals 195,that are carried by the respective cap members 25 and 27. The bearings193 are designed and adapted to provide both radial and axialpositioning, as well as load bearing. Any satisfactory conventionalbearing and bearing surface on shaft 101 may be employed. For example,the bearing may comprise a cylindrical roller bearing in combinationwith a thrust bearing cap; or frusto-conical roller bearings incombination with respective mating frusto-conical surfaces on the outputshaft 101.

The vane assembly 17 contains all of the elements delineatedhereinbefore and the individual vanes 113 are symmetrically contouredconcave inwardly as described hereinbefore. In this embodiment, however,the vane axle pin 111a is not a floating axle pin, but is retained invane shaft bearings 197 that are mounted at each end in the bearingpedestals 179 of the cap members 25 and 27. Thrust bearings 199 areprovided intermediate the two end knuckles 125a and the bearingpedestals 179 to prevent the edges, or longitudinal ends. 201 of thevanes from bearing hard against their mating surfaces. the inner facesof the circular plates 75a and 77a and the inner faces of the annularplates 83 and 85.

The flow through and torque control means comprise the adjustable inletaperture and the one or more adjustable discharge apertures, asdescribed with respect to the embodiment hereinbefore. In the embodimentillustrated in FIGS. and 11, however, the torque control sleeve 119a isreversible, as are the exhaust rings 149a, FIGS. -17.

The torque control sleeve 119a has the features delineated hereinbeforewith respect to torque control sleeve 119, but it has the gear toothrack 135 extended peripherally thereabout for a sufficient number ofdegrees to effect the positioning of the inlet slots 131 in thedischarge port 41 and the discharge slots 147 in the inlet port 31. Ihave found that a torque control sleeve 119a having the gear tooth rack135a extending for nearly 180 peripherally about the torque controlsleeve 119a provides satisfactory results. This extension is illustratedin the dashed line 203 of FIGS. 4, 5 and 6, since these figuresillustrate the essential positioning and relationships between the rotorassembly 15, the vane assembly 17 and the torque control sleeve 119 inthe three positions described hereinbefore; even though the crosssectional view of the remainder of the motor differs in the embodimentof FIG. 10. The means 133 for advancing and retarding the torque controlsleeve is otherwise essentially the same as described hereinbefore. FIG.11 illustrates the torque control sleeve 119a in the shut-off or zerotorque setting for reverse direction of rotation. Further movement ofthe torque control sleeve 119a counter clockwise provides control oftorque in the reverse direction of rotation.

The annular plates 83 and 85, serving as exhaust rings 1490 containingthe discharge slots 153, are emplaced within and retained within thecylindrical recess 204 interiorly of the flanges 23 with theirperipheral surfaces engaging the seal 151, as described hereinbefore.Retaining surfaces 205 are provided on the cap members 25 and 27 torotatably retain the annular plates 83 and 85 within their recess. Theexhaust rings 149a are angularly adjustable by the means 155, FIG. 15,as described hereinbefore. When the direction of rotation of the motor11 is reversed, however, the discharge slots 153 are positioned on theside of the vane assembly cavity 121 opposite the intake apertures whichnow communicate with the port 41, formerly referred to as the dischargeport and converted to an inlet port when the direction of rotation isreversed. To effect this degree of movement of the discharge slots 153,it is necessary that the gear tooth rack 157a, FIGS. l5-l7, extendcircumferentially of the exhaust rings 149a for about 150, instead ofthe lesser amount described hereinbefore, when the motor 11 was notreversible. The means for advancing and retarding the exhaust ring 149ais otherwise the same as described hereinbefore. FIGS. 15 and 16illustrate the exhaust rings 149a in the same relative positiondescribed hereinbefore with respect to FIGS. 8 and 9; namely, themaximum expansion position for FIG. 15 and the minimum expansionposition for FIG. 16, both in the forward direction. FIG. 17 illustratesthe exhaust ring in the reversing position.

FIG. 18 is an end view of one of the cap members, such as cap member 27,showing the discharge chamber 71, the discharge port in the form ofinternally threaded aperture 73, output shaft bearing 195, retainingsurface 205, bearings 227 and 229 in which the respective shafts 141 and163 are joumalled for advancing and retarding, respectively, the torquecontrol sleeve 119a and the exhaust rings 149a. Also illustrated are thebearing pedestals 179 containing the vane shaft bearings 197, the vanethrust bearings 199, and the rotor thrust bearings 183.

A system that enables reversing the motor 11 and thus obviating thenecessity for a transmission with its reversing gears and a clutch, isillustrated in FIG. 12. Therein, a source of working fluid 209 isconnected, as by suitable conduit 211 and a reversing valve 213 with themotor 11. The motor 11 is also connected via suitable conduit 215, thereversing valve 213, and conduit 216 with a low pressure receiver 217.

As indicated hereinbefore, the high pressure source 209 may comprisenaturally occurring high pressure sources such as geothermal steam wellsor a high pressure source of a vapor of a low entropy fluid such asemployed in an external combustion system. The low pressure receiver,similarly as indicated hereinbefore, may comprise the atmosphere, areceiving vessel, or a condenser. In an external combustion system, arecirculation means 219 will be employed to restore the working fluid toits high pressure in the high pressure source 209. As illustrated, therecirculation means is connected with the low pressure receiver viasuitable conduit, indicated by dashed lines 221. The recirculation means219 is also connected with the high pressure source 209 by suitableconduit, as indicated by the discontinuous dashed lines 223. A typicalrecirculation means comprises a pump and boiler, or vapor generator. Asillustrated in FlG.12, the fluid will flow from the high pressure sourceinto the inlet port 31, through motor 11, and from the discharge port 41to the low pressure receiver 217. On the other hand, the reversing valve213 may be positioned as illustrated in FIG. 13 to effect a reversedirection of flow in which the incoming fluid flows through conduit 211and thence through conduit 215 into the port 41 that served as thedischarge port in the forward direction of rotation; reversely throughthe motor 11 and thence from the port 31 that served as the inlet portin the forward direction of rotation outwardly to the low pressurereceiver 217 through conduit 216. Normally, it is advantageous toposition the reversing valve 213 in the cut-off position, as illustratedin FIG. 14, before reversing the direction of rotation of the motor 11,as will become apparent from the operational description laterhereinafter. The exhaust from the end caps 25 and 27 join downstream ofreversing valve 213 and is not affected by its position.

In normal forward operation, the working fluid flows from the highpressure source 209 through the reversing valve 213 and into the motor11 through the inlet port 31, as described hereinbefore. The expansionof the working fluid and the movement of the working fluid from the highpressure at the inlet aperture adjacent inlet port 31 to the dischargeports, in the form of either discharge slots 153 in exhaust rings 149aor discharge slots 147 in the torque control sleeve 119a, cause the vaneassembly to rotate. Rotation of the vane assembly, in turn, causesrotation of the rotor assembly 15. The rotor assembly 15 rotates thetorque output gear 177, driving the torque transmission gear 175 and theoutput shaft 101. The output shaft 101 engages suitable coupling meanssuch as internally splined coupling gear 225. The gear 225 is fittedinto the splined end 227 of the shaft 101 and serves as an intermediatedrive for driving suitable apparatus taking power from the output shaft101. Thus, this operation is functionally similar to the embodimentdescribed hereinbefore with respect to FIGS. 1-9 in normal operation.

To drive the motor 11 in the reverse direction, as for reversing theapparatus being driven from the gear 225, the reversing valve 213 ismoved into the shutoff position, stopping the flow of working fluid, asillustrated in FIG. 14. The torque control sleeve 119a is then movedinto the zero torque setting for reverse direction of rotation, asillustrated in FIG. 11. The exhaust ring 149a is moved to the reverseposition, as illustrated in FIG. 17; to locate the exhaust openings onthe opposite side of the motor from the normal forward rotationallocation. The reversing valve 213 is then moved to the reverse position,as illustrated in FIG. 13. Moving the torque control sleeve 119a counterclockwise in FIG. 11 then provides control of torque in the reversedirection of rotation. The ports serving as the inlet and dischargeports have now been reversed, or exchanged, one for the other. Theexhaust rings are normally retained in their indicated position duringreversing, since accurate control of the expansion losses may not becritical because the reversing operation is short lived, ordinarily.

To return to forward operation, the reversing valve 213 is moved to theshut-off position, as illustrated in FIG. 14, and the torque controlsleeve 119a and the exhaust rings 149a are moved to the normaloperational position, described hereinbefore. Thereafter, the reversingvalve 213 is moved to its normal operational position, as illustrated inFIG. 12 and forward rotation is again effected.

This embodiment can be operated in the supercharged condition, asdescribed with respect to the embodiment of FIGS. 1-9. This capabilityis very desirable where reversing of the motor is employed in order thatlarge power or high torque can be supplied as needed, even at a smallexpense in efficiency, where a low" gear ratio, or high torque, is notavailable via a transmission.

While the vanes have been described without a supplemental seal at theirtips, hard service may make it advantageous to employ vane tip shoeswhich float between the inner wall of the torque control sleeve 119a andthe vane tip, or end face, 115. The vane tip shoes encompass the vanetip and two sides, and curve to match the curvature of the internal wallof the torque control ring, as illustrated in FIG. 19. Therein, the shoeforms a separate seal 231 that is fitted on parallel sides 233 and 235that extend inwardly from the end of the vane tip, or end face, a shortdistance. The shoe, or seal, 231 sealingly engages the end of the vaneand slidably engages the parallel sides 233 and 235 such that it isthrown outwardly by centrifugal force into sealing engagement with thewall of the torque control sleeve 119a, without sacrificing the seal onthe sides of the vane 113. Such a seal 231 is employed, ordinarily, whena lubricant is injected into the fluid, or the fluid has at least somelubricating properties. If desired, the seal 231 may have a lubricantsuch as a fluorocarbon impregnated thereinto for applications in whichlubrication is not effected by the fluid flowing through the motor 11.

If desired, vane compression strips may be installed in one or moregrooves at the vane tip for effecting the desired seal. The vane tips,or any shoes that are employed, may be made from hard material forbetter wearing characteristics and less friction.

If desired, each respective follower means, or vane guides, may becantilevered from a single circular plate; although having the twocircular plates and having the vane guides affixed to each of the platesaffords a reinforced structure that is, ordinarily, more advantageous.Similarly, the shaft 103, FIG. 3, provides a better structure, but itmay be omitted if a cantilevered structure is desired.

The respective follower means may be retained intermediate the circularplates 75 and 77 by any other conventional means. For example, ifdesired, the vane guides 87 may be an integrally formed unit and theshaft portion 91 nested in suitable bearing means recessed in thecircular plates 75 and 77. The embodiment illustrated hereinbefore hasbeen found to be preferable because of the advantages attendant therespective rolling friction instead of requiring a sliding friction. Ifthe duty is unusually severe, the bearing insert 93 may be replaced byaircraft roller bearings or needle bearings for still further improvedperformance.

While knobs and fixed mounted pinion gears have been described in therespective means 133 and for advancing and retarding the torque controlsleeve 119 and the exhaust rings 149, it will be advantageous, wherepossible, to employ a controllable power means to effect the desireddegree of rotation of the pinion gears to effect the requisite angularpositioning of the sleeve 119 and the exhaust rings 149. Other entirelydifferent structures may be employed to effect the angular positioningthereof, if desired.

From the foregoing, it can be seen that this invention provides a basicstructure having improved seal characteristics that can be widelyemployed in motor and engine applications. Moreover, the inventionprovides an improved structure that can be employed without the expenseof the transmission and the like, since the motor has reversingcharacteristics in specific embodiments and since the motor can beemployed over a wide variety of applications with a wide variety ofworking fluids ranging from naturally occurring fluids to the lowentropy fluids that may be employed in external combustion power systemsto lessen the pollution in the gases discharged from the system.

The invention provides all of the objects delineated hereinbefore byproviding one or more of the desirable features delineated.Specifically, the invention provides a motor that has a sufficientlylarge number of vanes. preferably 8 or more, to allow effective use ofthe adjustable torque control sleeve and the adjustable exhaust ringswithout overlapping effects and to allow adjustment in inlet volume perrevolution so that the adjustable torque control sleeve may servecompletely as motor torque and speed control with a minimum of pressuredrop throttling of the torque control sleeve at the near-zero torquesettings. Having the larger number of vanes also greatly reducesleakage, since pressure drop across a given vane from one subchamber tothe next is inversely proportional to the number of vanes in a workingfluid expansion environment at any one time. Moreover, the forceconcentrations within the motor are also minimized by providing asufficient number of vanes that the output torque producing the forcesare distributed over at least three or four vane guides instead of oneor two. Motor 11 offers power to weight and power to size ratios thatare superior to any of the prior art expansion motors, including lowspeed turbines. by factors of from 3 to l to as much as 10 to l. Inaddition, the motor 11 offers potential efficiences virtuallyunsurpassed and operating characteristics heretofore unobtainable. Themanifold reasons for this surprisingly improved performance have beenexplained in detail hereinbefore and include: (1) the taking advantageof the double effects of conventional differential force on the vanesand of pseudo cranking action to effect torque and power output; and (2)the unusually great volume displacement per revolution of the motor 11,effected by the means in which the vane guides of the rotor assemblyinterdigitate the symmetrically contoured vane surfaces to cause extremeoscillatory differences in dimension during rotation for unusually largechange in the volume of each subchamber and because the vane guides moveinwardly and outwardly radially along the vanes for unusually largeradial distances to further increase the dimensional change of eachsubchamber.

Although the motor 11 is ideally suited for mobile equipmentapplications. such as driving an automobile, it has unique features thatenable replacing turbines with it in stationary applications;particularly. since it may be operated through the superheat region andwell into the saturated region for expansion of steam and similarfluids. Condensate formation within the motor will have little, if any,adverse effect on the motor 11. It can be operated completely within thesaturated region if desired. Thus, the motor will allow any Rankinecycle external combustion engine system, or other pressurized fluidsystem, to operate very near the ultimate available efficiency over theentire speed and power range of the motor. In nuclear Water heatingreactor power plants, where steam temperature and pressure are limited,this unit can probably replace the low pressure condensing turbines andprovide somewhat higher efficiencies, as well as appreciably lowerinitial costs in the plant.

Although this invention has been described with a certain degree ofparticularity, it is understood that the present disclosure is made onlyby way of example and that-numerous changes in the details ofconstruction and the combination and arrangement of parts may beresorted to without departing from the spirit and the scope of thisinvention.

What is claimed -is:

1. In an eccentric rotor, concentric vane motor device having:

a. a main chamber having therewithin a substantially cylindricalinterior surface that defines a vane assembly cavity;

b. first and second ports spaced around and communicating with said mainchamber and serving as inlet and discharge ports;

c. a plurality of angularly related radial vanes, independently pivotaland rotatable within said vane assembly cavity about a vane axistherewithin; said vanes occupying substantially the total radialdistance from said vane axis to said interior surface;

d. a rotor that is eccentrically mounted with respect to said vaneassembly cavity and rotatable about a rotor axis spaced from said vaneaxis; said rotor having follower means for interdigitating said vanesand effecting a change in volume of a subchamber intermediate respectivesaid vanes as said rotor and said vanes are rotated within said vaneassembly cavity; each subchamber being delineated by a pair ofconfronting vane faces and a corresponding follower means between saidvane faces and the interior surface and varying from a minimum volumewith the respectivefollower means having its outermost position withrespect to said vane axis, the minimum volume position being arbitrarilyreferred to as the zero degree position, to a maximum volume with therespective follower means at its innermost position with respect to saidvane axis, arbitrarily referred to as the position; and

a power delivery shaft connected with said rotor for delivering powerfrom said rotor; the improvement comprising an improved seal meansintermediate said vane and said follower means in which:

f. said follower means is disposed intermediate said respective vanesand comprises vane guides that are substantially cylindrical rollersextending longitudinally of said rotor and having respective vaneengaging surfaces on each side that are disposed symmetrically about andhave a predetermined radius of curvature with respect to the centralaxis of each respective vane guide;

g. said vanes have lateral faces that are concaved inwardly toward thecentral plane of the vane such that said follower means is maintained insubstantially uniform sealing engagement with said vane lateral faces assaid follower means traverse inwardly and outwardly therealong duringrotation of said rotor such that a satisfactory seal is maintainedintermediate said follower means and said vanes so that said followermeans can serve as a piston as well as an interdigitating means; saidvanes being symmetrically contoured with respect to said central planeof the vane such that each said respective vane maintains saidsatisfactory seal at their respective points of contact with adjacentvane guides; and I h. an integral and adjustable flow through and torquecontrol means for controlling torque output without requiring a throttleand the throttle-caused losses in efficiency.

2. The device of claim 1 wherein said vane guides are rotatably mountedin said rotor and intermediate respective said vanes such that theyserve, not only as a part of said improved seal means, but also as apiston for effecting a pseudo cranking action on said rotor assembly forunusually high torque and power output.

3. The device of claim 1 wherein said power delivery shaft comprises anelongate shaft traversing the length of said rotor assembly; a pair oftorque transmission gears are drivingly connected with said shaft atspaced apart locations adjacent each end of said rotor assembly toprovide a balanced power take-off for avoiding intolerable torsionaltwisting of large elongate rotor assemblies; said rotor assembly iselongate and has circular plates disposed at each end, said plates beingdrivingly connected with respective torque output gears that drivinglyengage said torque transmission gears; bearing supports are provided forsaid shaft at a plurality of locations therealong such that largeamounts of power can be delivered to said elongate shaft withoutdistorting said shaft sufficiently to induce intolerable vibrations; avane shaft is provided with said vanes pivotally mounted thereon; ahousing has ends enclosing said circular plates, bearing pedestalsmounted on each said end of said housing; and said vane shaft isjournalled in said bearing pedestals for great stability.

4. The device of claim 1 wherein said flow through and torque controlmeans comprises a single angularly adjustable torque control sleeve thatencompasses the length of the periphery and tips of said vanes and has aplurality of apertures extending the length of said torque controlsleeve and peripherally thereabout sufficient to subtend an anglegreater than 90 and no more than 180 with respect to the centrallongitudinal axis of said torque control sleeve; each said aperturehaving a cross sectional dimension peripherally of said torque controlsleeve less than the thickness of each vane tip so as to prevent flowback of a fluid around said vane tip and to prevent communication with aplurality of subchambers simultaneously; a first plurality of similarlyangularly disposed said apertures serving as inlet aperturescommunicating in normal operation between said vane assembly cavity andthe one port of said first and second ports serving as the inlet portsuch that advancing said torque control sleeve in a first direction willincrease the effective flow area through said inlet apertures and saidinlet port and retarding of said torque control sleeve in a seconddirection opposite said first direction will decrease the effective flowarea through said inlet apertures and said inlet port; said firstplurality being less than one-half of said plurality ofapertures; asecond plurality of similarly angularly disposed said apertures servingas discharge apertures communicating in normal operation between saidvane assembly cavity and the other port of said first and second portsserving as the discharge port; said second plurality being more thanone-half of said plurality of apertures; and a sealing portion of saidinternal surface of said main chamber sealingly engages said torquecontrol sleeve longitudinally thereof and any of said apertures includedbetween said inlet and discharge ports; said sealing portion being ofperipheral extent greater than that of a subchamber at its minimumvolume so as to prevent communication between said inlet and dischargeports by way of said apertures and said subchambers, yet allow flow offluids into and out of respective subchambers over their entire lengthfor optimum efficiency; and a means for advancing and retarding saidtorque control sleeve.

5. The device of claim 4 wherein said inlet apertures define a firstflow area with respect to said inlet port and said discharge aperturesdefine a second flow area with respect to said discharge port; and saidfirst and second flow areas are adjustable such that a greater volume offluid at the pressure exteriorly of said inlet apetures can flow throughsaid first area into said vane assembly cavity than can flow throughsaid second flow area from said vane assembly cavity at the pressureexteriorly of said discharge apertures; and such that superchargedoperation of said motor device is effected for greater power output byincreases in inlet loading work performed .and expansion work performedper revolution of said motor device at the expense of only a smallreduction in efficiency; and for effecting the desirable capability ofallowing direct driving of mobile equipment through a reduction gearwithout requiring a transmission having an adjustable ratio gear andclutch.

6. The device of claim 4 wherein said flow through and torque controlmeans also includes a discharge flow control means for controlling thevolumetric rate of flow of fluid through the discharge port of saidfirst and second ports such that pressure interiorly of said chamber canbe controlled and reduce losses from over-expansion and under-expansionof a working fluid flowing therethrough from a high pressure source to alow pressure receiver and such that a high efficiency can be effectedover a wide range of power and speed requirements.

7. The device of claim 6 wherein said discharge flow control meansincludes at least one adjustable exhaust ring disposed at at least oneend of said main chamber and having at least one discharge aperturecommunicating between a discharge port and said vane assembly cavitysuch that advancing said exhaust ring in a first direction will initiatethe discharge of working fluid from respective subchambers earlier interms of the angular displacement from the zero degree position andretarding said exhaust ring in the second direction opposite said firstdirection will retard the initiation of the discharge of working fluidfrom respective subchambers; and means for advancing and retarding saidexhaust ring.

8. The device of claim 7 wherein an exhaust ring is provided at each endof said main chamber for increasing the flow of working fluid from asubchamber during a discharge portion of each revolution of each saidsubchamber.

9. A system for drivingly powering a machine forwardly and reversely atthe option of an operator, without requiring a transmission thatincludes a clutch and reversing gears, comprising:

a. a high pressure source of working fluid at superatmospheric pressure;

b. a low pressure receiver means for receiving said working fluid at apressure that is sufficiently lower than said superatmospheric pressureto enable deriving useful work from said working fluid flowing from saidhigh pressure source through a motor device to said low pressurereceiver means;

c. an eccentric rotor, concentric vane motor device having:

i. a main chamber having therewithin a substantially cylindricalinterior surface that defines a vane assembly cavity;

ii. first and second ports spaced around and communicating with saidmain chamber and serving as inlet and discharge ports;

iii. a plurality of angularly related radial vanes, independentlypivotal and rotatable within said vane assembly cavity about a vane axistherewithin; said vanes occupying substantially the total radialdistance from said vane axis to said interior surface;

iv. a rotor that is eccentrically mounted with respect to said vaneassembly cavity and rotatable about a rotor axis spaced from said vaneaxis; said rotor having follower means intermediate respective saidvanes for interdigitating said vanes and effecting a change in volume ofa subchamber intermediate respective said vanes as said rotor and saidvanes are rotated within said vane assembly cavity; each subchamberbeing delineated by a pair of confronting vane faces and a correspondingfollower means between said vane faces and said interior surface andvarying from a minimum volume at the outer-most position of saidfollower means with respect to said vane axis to a maximum volume at theinnermost position of said follower means;

v. a power delivery shaft connected with said rotor for delivering powerfrom said rotor;

vi. a satisfactory seal means intermediate said vanes and said followermeans;

vii. an integral and adjustable flow through and torque control meansfor controlling torque output of said motor without requiring a throttleand the throttle-caused losses in efficiency; said flow through andtorque control means comprising:

A. an angularly adjustable torque control sleeve that encompasses theentire periphery and length of the periphery and tips of said vanes andhas a plurality of apertures extending the length of said torque controlsleeve and peripherally thereabout sufficient to subtend an are greaterthan 90 and no more than 180; each said aperture having a crosssectional dimension peripherally of said torque control sleeve less thanthe thickness of a vane tip so as to prevent flow back of a fluid aroundsaid vane tip and to prevent communication with a plurality ofsubchambers simultaneously; a first plurality of similarly angularlydisposed said apertures serving as inlet apertures communicating innormal operation between said vane assembly cavity and the one port ofsaid first and second ports serving as the inlet port such thatadvancing said torque control sleeve in a first direction will increasethe effective flow area through said inlet apertures and said inlet portand retarding said torque control sleeve in a second direction oppositesaid first direction will decrease the effective flow area through saidinlet apertures and said inlet ports; said first plurality being lessthan one-half of said plurality of apertures; a second plurality ofsimilarly angularly disposed said apertures serving as dischargeapertures communicating in normal operation between said vane assemblycavity and the other port of said first and second ports serving as thedischarge port; said second plurality being more than one-half of saidplurality of apertures; and a sealing portion of said internal surfaceof said main chamber sealingly engaging said torque control sleeve andany of said apertures included between said inlet and discharge ports;said sealing portion being of a peripheral extent greater than that of asubchamber at its minimum volume so as to prevent communication betweensaid inlet and discharge ports yet allow flow of fluids into and out ofrespective subchambers over their entire length; said torque controlsleeve being reversible so as to reverse the port communicating withsaid vane assembly cavity via the inlet apertures for reversing thedirection of rotation of said motor device; and B. a discharge flowcontrol means that includes adjustable exhaust rings disposed at theends of said main chamber for controlling the volumetric rate of flow offluid through the discharge port of said first and second ports suchthat pressure interiorly of said vane assembly cavity can be controlledand reduce losses from over-expansion and underexpansion of a workingfluid flowing therethrough from said high pressure source to said lowpressure receiver means; said exhaust rings having a plurality ofdischarge apertures communicating in normal operation between adischarge port in said vane assembly cavity such that advancing saidexhaust ring in a first direction will initiate the discharge of workingfluid from respective subchambers earlier in terms of the angulardisplacement from the minimum volume position and retarding said exhaustring in the second direction opposite said first direction will retardthe initiation of the discharge of working fluid from respectivesubchambers; said discharge flow control means being reversible so as toreverse the port communicating with said main chamber via said dischargeflow control means; and

viii. at least one means for reversingly positioning said torque controlsleeve and said discharge flow control means; and d. reversing valvemeans for controlling the direction of flow of said working fluidthrough said motor device between said source and said receiver means.

1. In an eccentric rotor, concentric vane motor device having: a. a mainchamber having therewithin a substantially cylindrical interior surfacethat defines a vane assembly cavity; b. first and second ports spacedaround and communicating with said main chamber and serving as inlet anddischarge ports; c. a plurality of angularly related radial vanes,independently pivotal and rotatable within said vane assembly cavityabout a vane axis therewithin; said vanes occupying substantially thetotal radial distance from said vane axis to said interior surface; d. arotor that is eccentrically mounted with respect to said vane assemblycavity and rotatable about a rotor axis spaced from said vane axis; saidrotor having follower means for interdigitating said vanes and effectinga change in volume of a subchamber intermediate respective said vanes assaid rotor and said vanes are rotated within said vane assembly cavity;each subchamber being delineated by a pair of confronting vane faces anda corresponding follower means between said vane faces and the interiorsurface and varying from a minimum volume with the respective followermeans having its outermost position with respect to said vane axis, theminimum volume position being arbitrarily referred to as the zero degreeposition, to a maximum volume with the respective follower means at itsinnermost position with respect to said vane axis, arbitrarily referredto as the 180* position; and e. a power delivery shaft connected withsaid rotor for delivering power from said rotor; the improvementcomprising an improved seal means intermediate said vane and saidfollower means in which: f. said follower means is disposed intermediatesaid respective vanes and comprises vane guides that are substantiallycylindrical rollers extending longitudinally of said rotor and havingrespective vane engaging surfaces on each side that are disposedsymmetrically about and have a predetermined radius of curvature withrespect to the central axis of each respective vane guide; g. said vaneshave lateral faces that are concaved inwardly toward the central pLaneof the vane such that said follower means is maintained in substantiallyuniform sealing engagement with said vane lateral faces as said followermeans traverse inwardly and outwardly therealong during rotation of saidrotor such that a satisfactory seal is maintained intermediate saidfollower means and said vanes so that said follower means can serve as apiston as well as an interdigitating means; said vanes beingsymmetrically contoured with respect to said central plane of the vanesuch that each said respective vane maintains said satisfactory seal attheir respective points of contact with adjacent vane guides; and h. anintegral and adjustable flow through and torque control means forcontrolling torque output without requiring a throttle and thethrottle-caused losses in efficiency.
 2. The device of claim 1 whereinsaid vane guides are rotatably mounted in said rotor and intermediaterespective said vanes such that they serve, not only as a part of saidimproved seal means, but also as a piston for effecting a pseudocranking action on said rotor assembly for unusually high torque andpower output.
 3. The device of claim 1 wherein said power delivery shaftcomprises an elongate shaft traversing the length of said rotorassembly; a pair of torque transmission gears are drivingly connectedwith said shaft at spaced apart locations adjacent each end of saidrotor assembly to provide a balanced power take-off for avoidingintolerable torsional twisting of large elongate rotor assemblies; saidrotor assembly is elongate and has circular plates disposed at each end,said plates being drivingly connected with respective torque outputgears that drivingly engage said torque transmission gears; bearingsupports are provided for said shaft at a plurality of locationstherealong such that large amounts of power can be delivered to saidelongate shaft without distorting said shaft sufficiently to induceintolerable vibrations; a vane shaft is provided with said vanespivotally mounted thereon; a housing has ends enclosing said circularplates, bearing pedestals mounted on each said end of said housing; andsaid vane shaft is journalled in said bearing pedestals for greatstability.
 4. The device of claim 1 wherein said flow through and torquecontrol means comprises a single angularly adjustable torque controlsleeve that encompasses the length of the periphery and tips of saidvanes and has a plurality of apertures extending the length of saidtorque control sleeve and peripherally thereabout sufficient to subtendan angle greater than 90* and no more than 180* with respect to thecentral longitudinal axis of said torque control sleeve; each saidaperture having a cross sectional dimension peripherally of said torquecontrol sleeve less than the thickness of each vane tip so as to preventflow back of a fluid around said vane tip and to prevent communicationwith a plurality of subchambers simultaneously; a first plurality ofsimilarly angularly disposed said apertures serving as inlet aperturescommunicating in normal operation between said vane assembly cavity andthe one port of said first and second ports serving as the inlet portsuch that advancing said torque control sleeve in a first direction willincrease the effective flow area through said inlet apertures and saidinlet port and retarding of said torque control sleeve in a seconddirection opposite said first direction will decrease the effective flowarea through said inlet apertures and said inlet port; said firstplurality being less than one-half of said plurality of apertures; asecond plurality of similarly angularly disposed said apertures servingas discharge apertures communicating in normal operation between saidvane assembly cavity and the other port of said first and second portsserving as the discharge port; said second plurality being more thanone-half of said plurality of apertures; and a sealing portion of saidinternal surface of said main chamber sealingLy engages said torquecontrol sleeve longitudinally thereof and any of said apertures includedbetween said inlet and discharge ports; said sealing portion being ofperipheral extent greater than that of a subchamber at its minimumvolume so as to prevent communication between said inlet and dischargeports by way of said apertures and said subchambers, yet allow flow offluids into and out of respective subchambers over their entire lengthfor optimum efficiency; and a means for advancing and retarding saidtorque control sleeve.
 5. The device of claim 4 wherein said inletapertures define a first flow area with respect to said inlet port andsaid discharge apertures define a second flow area with respect to saiddischarge port; and said first and second flow areas are adjustable suchthat a greater volume of fluid at the pressure exteriorly of said inletapetures can flow through said first area into said vane assembly cavitythan can flow through said second flow area from said vane assemblycavity at the pressure exteriorly of said discharge apertures; and suchthat supercharged operation of said motor device is effected for greaterpower output by increases in inlet loading work performed and expansionwork performed per revolution of said motor device at the expense ofonly a small reduction in efficiency; and for effecting the desirablecapability of allowing direct driving of mobile equipment through areduction gear without requiring a transmission having an adjustableratio gear and clutch.
 6. The device of claim 4 wherein said flowthrough and torque control means also includes a discharge flow controlmeans for controlling the volumetric rate of flow of fluid through thedischarge port of said first and second ports such that pressureinteriorly of said chamber can be controlled and reduce losses fromover-expansion and under-expansion of a working fluid flowingtherethrough from a high pressure source to a low pressure receiver andsuch that a high efficiency can be effected over a wide range of powerand speed requirements.
 7. The device of claim 6 wherein said dischargeflow control means includes at least one adjustable exhaust ringdisposed at at least one end of said main chamber and having at leastone discharge aperture communicating between a discharge port and saidvane assembly cavity such that advancing said exhaust ring in a firstdirection will initiate the discharge of working fluid from respectivesubchambers earlier in terms of the angular displacement from the zerodegree position and retarding said exhaust ring in the second directionopposite said first direction will retard the initiation of thedischarge of working fluid from respective subchambers; and means foradvancing and retarding said exhaust ring.
 8. The device of claim 7wherein an exhaust ring is provided at each end of said main chamber forincreasing the flow of working fluid from a subchamber during adischarge portion of each revolution of each said subchamber.
 9. Asystem for drivingly powering a machine forwardly and reversely at theoption of an operator, without requiring a transmission that includes aclutch and reversing gears, comprising: a. a high pressure source ofworking fluid at superatmospheric pressure; b. a low pressure receivermeans for receiving said working fluid at a pressure that issufficiently lower than said superatmospheric pressure to enablederiving useful work from said working fluid flowing from said highpressure source through a motor device to said low pressure receivermeans; c. an eccentric rotor, concentric vane motor device having: i. amain chamber having therewithin a substantially cylindrical interiorsurface that defines a vane assembly cavity; ii. first and second portsspaced around and communicating with said main chamber and serving asinlet and discharge ports; iii. a plurality of angularly related radialvanes, independently pivotal and rotatable within said vane assemblycavity aBout a vane axis therewithin; said vanes occupying substantiallythe total radial distance from said vane axis to said interior surface;iv. a rotor that is eccentrically mounted with respect to said vaneassembly cavity and rotatable about a rotor axis spaced from said vaneaxis; said rotor having follower means intermediate respective saidvanes for interdigitating said vanes and effecting a change in volume ofa subchamber intermediate respective said vanes as said rotor and saidvanes are rotated within said vane assembly cavity; each subchamberbeing delineated by a pair of confronting vane faces and a correspondingfollower means between said vane faces and said interior surface andvarying from a minimum volume at the outer-most position of saidfollower means with respect to said vane axis to a maximum volume at theinnermost position of said follower means; v. a power delivery shaftconnected with said rotor for delivering power from said rotor; vi. asatisfactory seal means intermediate said vanes and said follower means;vii. an integral and adjustable flow through and torque control meansfor controlling torque output of said motor without requiring a throttleand the throttle-caused losses in efficiency; said flow through andtorque control means comprising: A. an angularly adjustable torquecontrol sleeve that encompasses the entire periphery and length of theperiphery and tips of said vanes and has a plurality of aperturesextending the length of said torque control sleeve and peripherallythereabout sufficient to subtend an arc greater than 90* and no morethan 180*; each said aperture having a cross sectional dimensionperipherally of said torque control sleeve less than the thickness of avane tip so as to prevent flow back of a fluid around said vane tip andto prevent communication with a plurality of subchambers simultaneously;a first plurality of similarly angularly disposed said apertures servingas inlet apertures communicating in normal operation between said vaneassembly cavity and the one port of said first and second ports servingas the inlet port such that advancing said torque control sleeve in afirst direction will increase the effective flow area through said inletapertures and said inlet port and retarding said torque control sleevein a second direction opposite said first direction will decrease theeffective flow area through said inlet apertures and said inlet ports;said first plurality being less than one-half of said plurality ofapertures; a second plurality of similarly angularly disposed saidapertures serving as discharge apertures communicating in normaloperation between said vane assembly cavity and the other port of saidfirst and second ports serving as the discharge port; said secondplurality being more than one-half of said plurality of apertures; and asealing portion of said internal surface of said main chamber sealinglyengaging said torque control sleeve and any of said apertures includedbetween said inlet and discharge ports; said sealing portion being of aperipheral extent greater than that of a subchamber at its minimumvolume so as to prevent communication between said inlet and dischargeports yet allow flow of fluids into and out of respective subchambersover their entire length; said torque control sleeve being reversible soas to reverse the port communicating with said vane assembly cavity viathe inlet apertures for reversing the direction of rotation of saidmotor device; and B. a discharge flow control means that includesadjustable exhaust rings disposed at the ends of said main chamber forcontrolling the volumetric rate of flow of fluid through the dischargeport of said first and second ports such that pressure interiorly ofsaid vane assembly cavity can be controlled and reduce losses fromover-expansion and under-expansion of a working fluid flowingtherethrough from said high pressure source to said low pressurereceiver means; saiD exhaust rings having a plurality of dischargeapertures communicating in normal operation between a discharge port insaid vane assembly cavity such that advancing said exhaust ring in afirst direction will initiate the discharge of working fluid fromrespective subchambers earlier in terms of the angular displacement fromthe minimum volume position and retarding said exhaust ring in thesecond direction opposite said first direction will retard theinitiation of the discharge of working fluid from respectivesubchambers; said discharge flow control means being reversible so as toreverse the port communicating with said main chamber via said dischargeflow control means; and viii. at least one means for reversinglypositioning said torque control sleeve and said discharge flow controlmeans; and d. reversing valve means for controlling the direction offlow of said working fluid through said motor device between said sourceand said receiver means.